US8042656B2 - Disk brake - Google Patents

Disk brake Download PDF

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Publication number
US8042656B2
US8042656B2 US11/790,008 US79000807A US8042656B2 US 8042656 B2 US8042656 B2 US 8042656B2 US 79000807 A US79000807 A US 79000807A US 8042656 B2 US8042656 B2 US 8042656B2
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Prior art keywords
disk
reinforcements
pad
mounting member
connecting plate
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US11/790,008
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US20070251772A1 (en
Inventor
Satoru Tsurumi
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Hitachi Astemo Ltd
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Hitachi Ltd
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Assigned to HITACHI, LTD. reassignment HITACHI, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TSURUMI, SATORU
Publication of US20070251772A1 publication Critical patent/US20070251772A1/en
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Assigned to HITACHI ASTEMO, LTD. reassignment HITACHI ASTEMO, LTD. CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: HITACHI AUTOMOTIVE SYSTEMS, LTD.
Assigned to HITACHI AUTOMOTIVE SYSTEMS, LTD. reassignment HITACHI AUTOMOTIVE SYSTEMS, LTD. DEMERGER Assignors: HITACHI, LTD.
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0977—Springs made from sheet metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0972—Resilient means interposed between pads and supporting members or other brake parts transmitting brake reaction force, e.g. elements interposed between torque support plate and pad

Definitions

  • the present invention relates to a disk brake suitably used to apply braking force to a vehicle, for example, an automobile.
  • a disk brake provided on a vehicle e.g. an automobile is arranged as follows.
  • inner and outer friction pads are pressed against both sides of a disk, thereby applying braking force to the disk (for example, see Japanese Patent Application Publication No. 2003-222171).
  • This type of conventional disk brake includes a mounting member secured to a non-rotating part of a vehicle.
  • the mounting member has a pair of arms spaced apart from each other in the rotational direction of a disk.
  • the pair of arms extends over the outer periphery of the disk in the axial direction of the disk.
  • the arms are provided with pad guides formed, for example, from U-grooves.
  • a caliper is provided on the arms of the mounting member slidably in the axial direction of the disk.
  • a pair of friction pads is slidably fitted in the pad guides of each arm. The friction pads are adapted to be pressed against both sides of the disk by the caliper.
  • Two (for example) pad springs are attached respectively to the arms of the mounting member to resiliently support the pair of friction pads between the arms and to guide the friction pads in the axial direction of the disk.
  • Each pad spring is formed in a U shape as a whole from a resilient metal plate, for example, and disposed to extend over the outer periphery of the disk in the axial direction thereof from one (inner) side to the other (outer) side of the disk.
  • the pad spring has a pair of guide plates positioned at the inner and outer sides, respectively, of the disk and fitted into the respective pad guides of the mounting member and a connecting plate extending over the outer periphery of the disk in the axial direction thereof and connected at both ends thereof to the pair of guide plates.
  • the guide plates resiliently support the friction pads, respectively, in the pad guides of the mounting member, thereby suppressing rattling of the friction pads and allowing smooth sliding displacement thereof.
  • the connecting plate integrally connects together the inner and outer guide plates.
  • the above-described conventional technique uses substantially U-shaped pad springs to support the inner and outer friction pads.
  • This conventional structure involves some problems arising as the slidability of the friction pads relative to the pad springs deteriorates with age. That is, if the friction pads are caused to return away from the disk due to run-out of the disk rotating at idle during non-braking operation, external forces are applied to the guide plates of each pad spring in directions in which the guide plates are pulled away from the disk, together with the friction pads returned away from the disk.
  • the joints are elastically deformed.
  • the elastic deformation of the joints undesirably causes the friction pads to be always pressed toward the disk.
  • the friction pads thus pressed may drag against the disk, which causes brake noise or judder.
  • insufficient strength and rigidity of the joints between the guide plates and the connecting plate lead to degradation of the function and durability of the pad spring.
  • an object of the present invention is to provide a disk brake capable of satisfactorily increasing the strength of pad springs to prevent deformation thereof and to improve the durability and reliability thereof without the need to substantially change the configuration and the like of the pad springs.
  • a disk brake including a mounting member having a pair of arms spaced apart from each other in the rotational direction of a disk.
  • the arms extend over the outer periphery of the disk in the axial direction of the disk.
  • the arms are provided with pad guides.
  • a caliper is provided on the mounting member slidably in the axial direction of the disk.
  • a pair of friction pads is slidably fitted to the arms of the mounting member through the pad guides. The friction pads are adapted to be pressed against both sides of the disk by the caliper.
  • Pad springs are attached to the arms, respectively, of the mounting member to resiliently support the friction pads between the arms.
  • the pad springs each include a pair of guide plates positioned in the pad guides, respectively, of the mounting member at the axially opposite sides of the disk to guide the pair of friction pads in the axial direction of the disk.
  • Each pad spring further includes a connecting plate having a flat plate portion extending in the axial direction of the disk over the outer periphery thereof and two joint portions located at the opposite ends of the flat plate portion and joined to the pair of guide plates. Further, each pad spring has reinforcements provided on at least the two joint portions of the connecting plate to reinforce the joint portions.
  • the reinforcements may be formed from recessed projections.
  • the reinforcements may be provided on the flat plate portion and the two joint portions of the connecting plate.
  • the reinforcements may include a rectilinear reinforcement rectilinearly provided on the flat plate portion of the connecting plate and oblique reinforcements respectively provided on the two joint portions of the connecting plate to extend obliquely from the opposite ends of the rectilinear reinforcement toward the guide plates.
  • FIG. 1 is a general view of a disk brake according to a first embodiment of the present invention.
  • FIG. 2 is a bottom-view of the disk brake in FIG. 1 as seen from the outer side thereof.
  • FIG. 3 is a fragmentary enlarged view showing a pad guide, a pad spring and their vicinities in FIG. 2 .
  • FIG. 4 is a perspective view of a pad spring as a single element.
  • FIG. 5 is a front view of the pad spring.
  • FIG. 6 is a side view of the pad spring in FIG. 5 as seen from the right side thereof
  • FIG. 7 is a fragmentary enlarged view of part a in FIG. 5 .
  • FIG. 8 is an enlarged sectional view of a connecting plate, reinforcements and so forth of the pad spring as seen in the direction of the arrow VIII-VIII in FIG. 7 .
  • FIG. 9 is a fragmentary enlarged view of a disk brake according to a second embodiment of the present invention as seen from a position similar to that of FIG. 7 .
  • FIG. 10 is a fragmentary enlarged view of a disk brake according to a third embodiment of the present invention as seen from a position similar to that of FIG. 7 .
  • FIG. 11 is a general view of a disk brake according to a fourth embodiment of the present invention.
  • FIG. 12 is a rear view of a pad spring shown in FIG. 11 .
  • FIG. 13 is a side view of the pad spring in FIG. 12 as seen from the left side thereof.
  • FIG. 14 is a general view of a disk brake according to a fifth embodiment of the present invention.
  • FIG. 15 is a rear view of a pad spring shown in FIG. 14 .
  • FIG. 16 is a side view of the pad spring in FIG. 15 as seen from the left side thereof.
  • FIG. 17 is a fragmentary enlarged view of a disk brake according to a sixth embodiment of the present invention as seen from a position similar to that of FIG. 7 .
  • FIGS. 1 to 8 show a first embodiment of the present invention.
  • a disk brake for use in an automobile will be explained by way of example.
  • a mounting member 1 is secured to a non-rotating part of a vehicle. As shown in FIGS. 1 and 2 , the mounting member 1 is positioned near a disk D that rotates in the direction of the arrow A, together with a wheel (not shown) of the vehicle. In this case, the disk D rotates in the arrow A direction when the vehicle runs in the forward direction.
  • the mounting member 1 consists essentially of a pair of arms 1 A, 1 A, a mounting seat portion 1 B, and a bow-shaped reinforcing beam 1 C.
  • the arms 1 A are spaced apart from each other in the rotational (circumferential) direction of the disk D and extend over the outer periphery of the disk D in the axial direction of the disk D.
  • the mounting seat portion 1 B connects together the proximal ends of the arms 1 A and is secured to the non-rotating part of the vehicle at the inner side of the disk D.
  • the reinforcing beam 1 C connects together the distal ends of the arms 1 A.
  • the arms 1 A are provided with respective pin holes 1 D (only one of them is shown) in which sliding pins 5 (described later) are slidably fitted, respectively.
  • Each pin hole 1 D is open on the end surface of the arm 1 A.
  • the pin hole 1 D is enlarged in diameter at the open end thereof to form an annular boot fitting groove 1 E surrounding the pin hole 1 D.
  • the distal end portion of a protective boot 6 (described later) is fitted in the boot fitting groove 1 E.
  • the portion of each arm 1 A in which the protective boot 6 is fitted has an outer diameter larger than that of the rest of the arm 1 A by an amount corresponding to the boot fitting groove 1 E.
  • Each arm 1 A has inner pad guides 2 , 2 (described later) formed at one (inner) of the axially opposite sides of the disk D and outer pad guides 2 , 2 at the other (outer) of the axially opposite sides (only the outer pad guides are shown).
  • the pad guides 2 are provided on the inner and outer sides, respectively, of each arm 1 A of the mounting member 1 .
  • the pad guides 2 are fitted with projections 7 A of friction pads 7 (described later) through pad springs 8 , respectively.
  • the pad guides 2 guide the friction pads 7 in the axial direction of the disk D when the brakes are applied or released.
  • the pad guides 2 are formed as U-grooves having a U-shaped sectional configuration, for example, and extend in the axial direction of the disk D.
  • the bottoms of the grooves constituting the pad guides 2 function as torque receiving portions that bear braking torque applied to the friction pads 7 from the disk D during a braking operation through the projections 7 A.
  • a caliper 3 is slidably provided on the mounting member 1 .
  • the caliper 3 has an inner leg portion 3 A provided at one side (inner side) of the disk D, a bridge portion 3 B extending from the inner leg portion 3 A to the other side (outer side) of the disk D over the outer periphery of the disk D between the arms 1 A of the mounting member 1 , and an outer leg portion 3 C extending radially inward of the disk D from the distal (outer) end of the bridge portion 3 B and bifurcated at the distal end thereof.
  • the inner leg portion 3 A is provided with a pair of mounting portions 3 D, 3 D projecting leftward and rightward, respectively, in FIG. 1 .
  • the mounting portions 3 D are slidably supported by the arms 1 A of the mounting member 1 through respective sliding pins 5 (described later).
  • the inner leg portion 3 A is provided with a cylinder 3 E that is externally supplied with a brake fluid pressure.
  • a piston 4 is slidably fitted in the cylinder 3 E.
  • sliding pins 5 between the mounting member 1 and the caliper 3 .
  • the sliding pins 5 are, as shown in FIG. 1 , fastened at the proximal ends thereof to the mounting portions 3 D of the caliper 3 by using bolts 5 A, etc.
  • the distal ends of the sliding pins 5 are slidably fitted in the respective pin holes 1 D of the arms 1 A of the mounting member 1 .
  • the caliper 3 is slidably supported by the mounting member 1 through the sliding pins 5 .
  • Protective boots 6 are provided between the sliding pins 5 and the arms 1 A of the mounting member 1 .
  • the protective boots 6 are each formed from an elastic material, e.g. rubber, in the shape of an axially extensible tubular member.
  • the protective boots 6 are fitted on the respective outer peripheries of the sliding pins 5 to seal between the outer peripheral surfaces of the sliding pins 5 and the pin holes 1 D of the mounting member 1 . More specifically, the protective boots 6 are secured at their proximal ends to the outer peripheries of the sliding pins 5 and fitted at their distal ends into the boot fitting grooves 1 E of the arms 1 A of the mounting member 1 .
  • Inner and outer friction pads 7 are positioned at the opposite (inner and outer) sides of the disk D.
  • Each friction pad 7 is formed, for example, as a substantially fan-shaped plate member extending in the rotational direction of the disk D. As shown in FIGS. 2 and 3 , each friction pad 7 has substantially quadrangular projections 7 A at the longitudinally opposite ends of the back side (backing plate) thereof.
  • the projections 7 A are spaced apart from each other in the rotational direction of the disk D.
  • the projections 7 A are slidably fitted in the pad guides 2 , respectively, of the mounting member 1 with guide plates 9 of pad springs 8 (described later) interposed therebetween. In this state, each projection 7 A is resiliently supported (held) between a top plate 9 A and a radially urging portion 12 of the associated pad spring 8 .
  • the inner and outer friction pads 7 are pressed against both sides of the disk D by the caliper 3 .
  • the projections 7 A are slidingly displaced along the pad guides 2 in the axial direction of the disk D.
  • each friction pad 7 receives braking torque from the disk D.
  • the braking torque causes the projection 7 A to be pressed against the groove bottom of the pad guide 2 through the guide plate 9 (side plate 9 C) of the pad spring 8 .
  • the braking torque is borne by the mounting member 1 .
  • a pair of pad springs 8 is provided on the arms 1 A, respectively, of the mounting member 1 .
  • the pad springs 8 are disposed at the opposite side across the friction pads 7 in the rotational direction of the disk D to resiliently support the inner and outer friction pads 7 and to allow smooth sliding displacement of the friction pads 7 .
  • the pad springs 8 are, as shown in FIGS. 4 to 6 , each integrally formed as a substantially U-shaped plate member by bending a resilient stainless steel plate, for example, by press working or other method.
  • the pad springs 8 extend over the outer periphery of the disk D from one side to the other of the disk D (i.e. from the inner side to the outer side of the disk D).
  • the pad springs 8 each have guide plates 9 , 9 , a connecting plate 10 , radially urging portions 12 , 12 , circumferentially urging portions 13 , 13 , reinforcement 15 , etc., which will be described below.
  • a pair of guide plates 9 is provided at the axially opposite sides, respectively, of the disk D to guide the friction pads 7 in the axial direction of the disk D.
  • the guide plates 9 are bent in a substantially U shape or “]” shape, for example, and fitted in the pad guides 2 , respectively, of the mounting member 1 to axially slidably support the projections 7 A of the friction pads 7 .
  • the guide plates 9 each have a top plate 9 A provided at a radially outer position in the associated pad guide 2 as viewed in the radial direction of the disk D, a bottom plate 9 B provided at a radially inner position in the pad guide 2 , a side plate 9 C connecting between the top plate 9 A and the bottom plate 9 B and placed to abut against the groove bottom of the pad guide 2 , and a rising plate 9 D rising from the end of the top plate 9 A radially outward of the disk D along the arm 1 A of the mounting member 1 , being bent in a substantially L shape.
  • the top plate 9 A, the bottom plate 9 B and the side plate 9 C surround the projection 7 A of the friction pad 7 in the pad guide 2 .
  • a connecting plate 10 is provided between the inner and outer guide plates 9 .
  • the connecting plate 10 is positioned, for example, in a gap S between the arm 1 A of the mounting member 1 and the bridge portion 3 B of the caliper 3 . At this position, the connecting plate 10 connects the inner and outer guide plates 9 to each other.
  • the connecting plate 10 is, as shown in FIGS. 4 and 5 , formed from an elongated plate material or the like having a substantially U-shaped (or “]”-shaped) outer shape, for example.
  • the connecting plate 10 is joined to the rising plates 9 D of the guide plates 9 in the state of obliquely bent relative to the rising plates 9 D.
  • the connecting plate 10 has a rectilinear flat plate portion 10 A extending in the axial direction of the disk D from one side to the other side thereof over the outer periphery of the disk D and two joint portions 10 B integrally formed at the longitudinally opposite ends of the flat plate portion 10 A and joined to the inner guide plate 9 and the outer guide plate 9 , respectively.
  • the flat plate portion 10 A has an engagement plate 11 (described later) integrally formed thereon at the middle in the longitudinal direction thereof.
  • the two joint portions 10 B are, as shown in FIG. 7 , bent from the opposite ends of the flat plate portion 10 A radially inward of the disk D in a substantially “ ⁇ ” shape and extend obliquely relative to the extension direction of the flat plate portion 10 A (i.e. the axial direction of the disk D).
  • the joint portions 10 B each have a predetermined width W that is smaller than that of the flat plate portion 10 A.
  • the distal ends of the joint portions 10 B are joined to the respective rising plates 9 D of the guide plates 9 .
  • the joints between the joint portions 10 B and the rising plates 9 D are bent in a substantially “ ⁇ ” shape relative to the rotational (circumferential) direction of the disk D.
  • An engagement plate 11 is provided at the middle in the longitudinal direction of the flat plate portion 10 A of the connecting plate 10 .
  • the engagement plate 11 is bent in a substantially “ ⁇ ” shape while extending downward from the flat plate portion 10 A.
  • the engagement plate 11 is engaged and secured to the radially inner side (i.e. disk pass portion) of the mounting member 1 , thereby positioning the pad spring 8 with respect to the mounting member 1 in the axial direction of the disk D.
  • Radially urging portions 12 are provided on the respective bottom plates 9 B of the guide plates 9 to urge the friction pads 7 radially outward of the disk D, thereby suppressing rattling and other undesired movement of the friction pads 7 .
  • Each radially urging portion 12 is, as shown in FIG. 4 , bent from the end of the bottom plate 9 B toward the inside of the guide plate 9 in a substantially U or C shape.
  • elastic deformation of the radially urging portion 12 allows the distal end thereof to move toward and away from the top plate 9 A.
  • the radially urging portion 12 urges the projection 7 A of the friction pad 7 toward the top plate 9 A of the guide plate 9 , thereby resiliently supporting the projection 7 A between the top plate 9 A and the radially urging portion 12 .
  • Circumferentially urging portions 13 are provided on the respective bottom plates 9 B of the guide plates 9 to urge the inner and outer friction pads 7 in the rotational (circumferential) direction of the disk D.
  • the circumferentially urging portions 13 are bent from the respective distal ends of the bottom plates 9 B of the guide plates 9 obliquely radially inward of the disk D.
  • Each circumferentially urging portion 13 is formed as a wide plate-shaped spring member bent in a “ ⁇ ” shape over the entire widthwise length thereof. The bent part of the circumferentially urging portion 13 is resiliently abutted against the end surface of the friction pad 7 .
  • Claw portions 14 are provided on the respective side plates 9 C of the guide plates 9 .
  • the claw portions 14 are engaged with the peripheral walls of the pad guides 2 in an elastically deformed state, whereby the guide plates 9 are held in the pad guides 2 so as not to fall off.
  • Reinforcement 15 is provided to extend over from the flat plate portion 10 A to the joint portions 10 B of the connecting plate 10 , for example, to increase the strength (e.g. bending strength) and rigidity of the pad spring 8 between the inner and outer guide plates 9 .
  • the reinforcement 15 is formed by a method, for example, embossing, at the same time when the pad spring 8 is formed by press working. As shown in FIGS. 7 and 8 , the reinforcement 15 is formed as a recessed projection that is recessed and projecting relative to the connecting plate 10 (e.g. as a region having a sectional configuration projecting from one side surface of the connecting plate 10 and recessed from the other side surface as shown in FIG. 8 , or as a region having a sectional configuration recessed from one side surface of the connecting plate 10 and projecting from the other side surface inversely to the configuration shown in FIG. 8 ).
  • a recessed projection that is recessed and projecting relative to the connecting plate 10 (e.g. as a region having a sectional configuration projecting from one side surface of the connecting plate 10 and recessed from the other side surface as shown in FIG. 8 , or as a region having a sectional configuration recessed from one side surface of the connecting plate 10 and projecting from the other side surface inversely to the configuration shown in
  • the reinforcement 15 includes a rectilinear reinforcement 15 A provided rectilinearly along the flat plate portion 10 A of the connecting plate 10 and a pair of oblique reinforcements 15 B, 15 B obliquely extending rectilinearly from the opposite ends of the rectilinear reinforcement 15 A toward the inner and outer guide plates 9 .
  • the distal ends of the pair of oblique reinforcements 15 B, 15 B that extend toward the guide plates 9 terminate short of the bends between the joint portions 10 B and the rising plates 9 D of the guide plates 9 to avoid interference with the bending operation for forming the bends.
  • the rectilinear reinforcement 15 A reinforces the flat plate portion 10 A of the connecting plate 10 .
  • the oblique reinforcements 15 B reinforce the inner and outer joint portions 10 B, respectively.
  • the oblique reinforcements 15 B extend to diverge from each other from the opposite ends of the rectilinear reinforcement 15 A in a splayed pattern (like drooping eyebrows).
  • the rectilinear reinforcement 15 A and the oblique reinforcements 15 B are formed contiguously with each other as an integral recessed projection and bent in a substantially U shape (or “]” shape) as a whole. Consequently, the reinforcement 15 can impart high strength and rigidity to the connecting plate 10 and its vicinities by synergy of the rectilinear reinforcement 15 A and the oblique reinforcements 15 B.
  • the disk brake according to this embodiment is arranged as stated above.
  • the disk brake operates as follows.
  • the inner and outer friction pads 7 can apply braking forces to the disk D from both sides thereof.
  • the supply of the fluid pressure into the cylinder 3 E is stopped. Consequently, the inner and outer friction pads 7 separate from the disk D and return to their non-braking positions.
  • the friction pads 7 may be dragged by the disk D and thus displaced in the rotational direction of the disk D, and the caliper 3 that presses the friction pads 7 may be displaced in the rotational direction by receiving counterforce from the disk D.
  • each pad spring 8 urges the friction pads 7 radially outward of the disk D with the radially urging portions 12 , and while doing so, urges the friction pads 7 in the rotational direction of the disk D with the circumferentially urging portions 13 . Therefore, if the friction pads 7 are displaced away from the disk D due to run-out of the disk D rotating at idle during non-braking operation, for example, in a state where the slidability of the friction pads 7 relative to the pad springs 8 has deteriorated with age, it is likely that external forces may be applied to the pad springs 8 according to the displacements of the friction pads 7 .
  • the external forces may urge the guide plates 9 of each pad spring 8 to move away from each other and act as forces that pull the opposite ends of the connecting plate 10 away from each other (i.e. in the directions of the arrows F, F in FIG. 5 ).
  • the connecting plate 10 is reinforced as a whole by the reinforcement 15 .
  • the vicinities of the joint portions 10 B are reinforced to have sufficient strength and rigidity by the oblique reinforcements 15 B. Therefore, the joint portions 10 B and so forth can be surely prevented from being deformed or damaged by external forces.
  • the connecting plate 10 of each pad spring 8 is provided with the reinforcement 15 having the rectilinear reinforcement 15 A and the oblique reinforcements 15 B. Therefore, the flat plate portion 10 A of the connecting plate 10 can be reinforced by the rectilinear reinforcement 15 A, and the joint portions 10 B can be surely reinforced by the oblique reinforcements 15 B.
  • the joint portions 10 B can be prevented from being distorted or deformed by the external forces. Therefore, the pad springs 8 can exhibit their functions stably for an increased period of time, and the durability and reliability thereof can be improved.
  • the increased rigidity of the joint portions 10 B and so forth can suppress deformation, positional displacement and the like of the guide plates 9 . Consequently, when the brake is activated and released, the friction pads 7 can be smoothly displaced in the axial direction of the disk D along the guide plates 9 , and thus it is possible to minimize the dragging torque and the like of the friction pads 7 and to improve the brake performance. Further, during assembling of the disk brake, the pad springs 8 are unlikely to be deformed even if somewhat strong force is applied thereto to assemble them into the disk brake. Accordingly, the assembling operation can be performed efficiently.
  • the pad springs 8 are formed by press working, for example, in this embodiment, it is possible to use a die or the like previously formed with a recessed projection profile for forming reinforcement. With this die, each pad spring 8 is formed, and while doing so, the reinforcement 15 having a recessed projection configuration can be formed by embossing.
  • the press forming of the pad spring 8 and the formation of the reinforcement 15 can be efficiently performed in the same process. Accordingly, the required strength and rigidity can be readily obtained without the need to complicate the equipment, process, etc. for forming the pad springs 8 , for example. Hence, it is possible to minimize the cost increase and to increase productivity.
  • each pad spring 8 is positioned in a narrow gap S (see FIG. 3 ) between the arm 1 A of the mounting member 1 and the caliper 3 . It is often difficult in the gap S to bend the connecting plate 10 to a considerable extent in the direction of the plate thickness to ensure the required strength, for example, due to the restriction on the layout of the surrounding component parts.
  • each joint portion 10 B it is also conceivable to increase the width W (see FIG. 7 ) of each joint portion 10 B, for example, to thereby ensure the required strength. In this case also, however, it may be difficult to widen the width W due to the restriction on the layout and so forth.
  • the connecting plate 10 is, as shown in FIG. 1 , positioned near a portion of the associated arm 1 A of the mounting member 1 corresponding to the boot fitting groove 1 E.
  • This portion of the arm 1 A has a larger diameter than the other portion thereof by an amount corresponding to the boot fitting groove 1 E. Therefore, if the width W of the joint portion 10 B located at the upper side as viewed in FIG. 1 , for example, is widened, the joint portion 10 B may interfere with the outer peripheral surface of the arm 1 A. Thus, there are cases where it is difficult to widen the joint portion 10 B.
  • the joint portions 10 B are embossed to form oblique reinforcements 15 B as in this embodiment, the strength and rigidity of the joint portions 10 B can be sufficiently increased without the need to widen the width W thereof. Accordingly, it is possible to readily design the component part shape of the pad springs 8 and the layout of the components without worrying about the interference between the connecting plate 10 and the arm 1 A, for example, in designing the disk brake.
  • the reinforcement 15 is provided with the oblique reinforcements 15 B obliquely extending from the opposite ends of the rectilinear reinforcement 15 A. Therefore, the rectilinear reinforcement 15 A and each oblique reinforcement 15 B can be extended contiguously. Accordingly, the reinforcement 15 can be formed in a substantially U or “]” shape as a whole.
  • the reinforcement 15 can reinforce the pad spring 8 over the entire area from the connecting plate 10 to its vicinities (i.e. the joints between the connecting plate and the inner and outer guide plates 9 ) by synergy of the rectilinear reinforcement 15 A and the oblique reinforcements 15 B.
  • the overall bending strength and the like of these portions of the pad spring 8 can be further increased.
  • FIG. 9 shows a second embodiment of the present invention.
  • the feature of this embodiment resides in that the reinforcement of each pad spring has a rectilinear reinforcement and each oblique reinforcement joined together in a substantially cross-shape configuration.
  • the same constituent elements as those in the foregoing first embodiment are denoted by the same reference numerals as used in the first embodiment, and a description thereof is omitted.
  • Each pad spring 8 has reinforcement 21 provided on the connecting plate 10 thereof.
  • the reinforcement 21 is formed as a recessed projection by a method, for example, embossing, substantially in the same way as in the first embodiment.
  • the reinforcement 21 includes a rectilinear reinforcement 21 A and a pair of oblique reinforcements 21 B.
  • the rectilinear reinforcement 21 A is longer than in the first embodiment, and the opposite ends thereof reach the opposite side end surfaces of the flat plate portion 10 A of the connecting plate 10 beyond the positions of the oblique reinforcements 21 B.
  • the oblique reinforcements 21 B are joined to the rectilinear reinforcement 21 A at respective positions near the opposite ends of the latter in the state of intersecting the rectilinear reinforcement 21 A in a substantially cross-shape configuration.
  • the second embodiment arranged as stated above can also offer substantially the same advantageous effects as those in the first embodiment.
  • the rectilinear reinforcement 21 A and the oblique reinforcements 21 B of the reinforcement 21 are joined in the state of intersecting each other in a substantially cross-shape configuration. Therefore, the bending strength of the joint portions 10 B and their vicinities of the connecting plate 10 can be further increased.
  • FIG. 10 shows a third embodiment of the present invention.
  • the feature of this embodiment resides in that the rectilinear reinforcement and the oblique reinforcements are disposed separately from each other. It should be noted that in this embodiment the same constituent elements as those in the first embodiment are denoted by the same reference numerals as used in the first embodiment, and a description thereof is omitted.
  • Each pad spring 8 has reinforcement 31 provided on the connecting plate 10 thereof.
  • the reinforcement 31 is formed as a recessed projection by a method, for example, embossing, substantially in the same way as in the first embodiment.
  • the reinforcement 31 includes a rectilinear reinforcement 31 A provided on the flat plate portion 10 A and a pair of oblique reinforcements 31 B provided rectilinearly on the joint portions 10 B, respectively.
  • the inner and outer oblique reinforcements 31 B are, however, disposed apart from the rectilinear reinforcement 31 A at an appropriate distance and formed from respective recessed projections that are separate from the rectilinear reinforcement 31 A.
  • the oblique reinforcements 31 B extend as far as the flat plate portion 10 A beyond a weak-strength portion (indicated by the straight line X-X in FIG. 10 ) at the joint between the flat plate portion 10 A and each joint portion 10 B. With this arrangement, the bending strength of the portion indicated by the straight line X-X can be increased.
  • the third embodiment arranged as stated above can also offer substantially the same advantageous effects as those in the first embodiment.
  • the rectilinear reinforcement 31 A and the oblique reinforcements 31 B of the reinforcement 31 are disposed separately from each other. Accordingly, the positions where the oblique reinforcements 31 B are formed can be readily adjusted according, for example, to the positional relationship between the oblique reinforcements 31 B and component parts installed around the pad spring 8 . Hence, the design freedom can be increased.
  • FIGS. 11 to 13 show a fourth embodiment of the present invention.
  • the feature of this embodiment resides in that the present invention is applied to a disk brake of the twin-bore specifications.
  • a mounting member 41 is secured to a non-rotating part of a vehicle.
  • the mounting member 41 is arranged substantially in the same way as in the first embodiment. That is, the mounting member 41 has a pair of arms 41 A, a mounting seat portion 41 B, a reinforcing beam 41 C, etc.
  • Each arm 41 A has U-groove shaped pad guides 42 positioned at the inner and outer sides, respectively, of a disk D.
  • a caliper 43 is slidably provided on the mounting member 41 through sliding pins (not shown).
  • the caliper 43 has an inner leg portion (not shown), a bridge portion 43 B, an outer leg portion 43 C, mounting portions 43 D, etc. substantially in the same way as in the first embodiment.
  • the inner leg portion is provided with two (for example) cylinders, and pistons are slidably fitted in the cylinders, respectively.
  • Inner and outer friction pads 44 are disposed at the opposite sides of the disk D.
  • Each friction pad 44 has substantially quadrangular projections 44 A respectively provided at both longitudinal ends thereof substantially in the same way as in the first embodiment.
  • the projections 44 A are slidably fitted in the pad guides 42 , respectively, of the mounting member 41 with guide plates 46 of pad springs 45 (described later) interposed therebetween.
  • each pad spring 45 consists essentially of guide plates 46 , a connecting plate 47 , an engagement plate 48 , radially urging portions 49 , claw portions 50 , and reinforcement 51 (described later) substantially in the same way as in the first embodiment.
  • the guide plates 46 each have a top plate 46 A, a bottom plate 46 B, a side plate 46 C, a rising plate 46 D, etc.
  • the connecting plate 47 has a flat plate portion 47 A and two joint portions 47 B.
  • Each pad spring 45 has reinforcement 51 provided on the connecting plate 47 thereof.
  • the reinforcement 51 is formed as a recessed projection having a substantially U or “]” shape as a whole by a method, for example, embossing, substantially in the same way as in the first embodiment.
  • the reinforcement 51 includes a rectilinear reinforcement 51 A provided on the flat plate portion 47 A and a pair of oblique reinforcements 51 B provided on the joint portions 47 B, respectively.
  • the fourth embodiment arranged as stated above can also offer substantially the same advantageous effects as those in the first embodiment.
  • the present invention is also applicable to a disk brake of the twin-bore specifications.
  • FIGS. 14 to 16 show a fifth embodiment of the present invention.
  • the feature of this embodiment resides in that the present invention is applied to a disk brake of specifications different from those described above.
  • a mounting member 61 is secured to a non-rotating part of a vehicle.
  • the mounting member 61 is arranged substantially in the same way as in the first embodiment. That is, the mounting member 61 has a pair of arms 61 A and a mounting seat portion 61 B.
  • Each arm 61 A has pad guides 62 positioned at the inner and outer sides, respectively, of a disk D.
  • the pad guides 62 are each formed as an L-shaped stepped portion, for example.
  • a caliper 63 is slidably provided on the mounting member 61 through sliding pins (not shown).
  • the caliper 63 has an inner leg portion 63 A, a bridge portion 63 B, an outer leg portion 63 C, mounting portions 63 D, a cylinder 63 E, etc. substantially in the same way as in the first embodiment.
  • the cylinder 63 E has a piston 64 slidably fitted therein.
  • Inner and outer friction pads 65 are disposed at the opposite (inner and outer) sides of the disk D.
  • the friction pads 65 are slidably supported by the pad guides 62 , respectively, of the mounting member 61 with respective guide plates 67 of pad springs 66 (described later) interposed therebetween.
  • the friction pads 65 are displaceable in the axial direction of the disk D.
  • each pad spring 66 has guide plates 67 , a connecting plate 68 , an engagement plate 69 , radially urging portions 70 , reinforcement 71 , etc., which will be described later, substantially in the same way as in the first embodiment.
  • a pair of guide plates 67 is provided at the axially opposite sides, respectively, of the disk D to guide the friction pads 65 in the axial direction of the disk D substantially in the same way as in the first embodiment.
  • the guide plates 67 are bent in an L shape, for example.
  • the outer surfaces of the guide plates are positioned along the associated pad guides 62 of the mounting member 61 .
  • the inner surfaces of the guide plates 67 are positioned along the radially inner end surfaces of the friction pads 65 , for example, to resiliently support the friction pads 65 between themselves and the associated radially urging portions 70 .
  • a connecting plate 68 is provided to connect between the inner and outer guide plates 67 .
  • the connecting plate 68 has a rectilinear flat plate portion 68 A extending in the axial direction of the disk D over the outer periphery thereof and two joint portions 68 B integrally formed at the longitudinally opposite ends of the flat plate portion 68 A and joined to the inner and outer guide plates 67 , respectively.
  • the flat plate portion 68 A has an engagement plate 69 integrally formed at the middle in the longitudinal direction thereof.
  • the engagement plate 69 is bent in a substantially “ ⁇ ” shape while extending downward from the flat plate portion 68 A.
  • Inner and outer radially urging portions 70 are provided radially outside the connecting plate 68 .
  • the radially urging portions 70 are formed as bent portions of substantially U shape, for example, and disposed at respective positions corresponding to the inner and outer friction pads 65 .
  • the distal ends of the radially urging portions 70 are folded from the connecting plate 68 radially inward of the disk D to abut resiliently against the radially outer end surfaces of the friction pads 65 .
  • the radially urging portions 70 urge the friction pads 65 radially inward and resiliently press them against the pad guides 62 .
  • Each pad spring 66 has reinforcement 71 provided on the connecting plate 68 thereof.
  • the reinforcement 71 is formed as a recessed projection having a substantially U or “]” shape as a whole by a method, for example, embossing, substantially in the same way as in the first embodiment.
  • the reinforcement 71 includes a rectilinear reinforcement 71 A provided on the flat plate portion 68 A and a pair of oblique reinforcements 71 B provided on the joint portions 68 B, respectively.
  • the fifth embodiment arranged as stated above can also offer substantially the same advantageous effects as those in the first embodiment.
  • FIG. 17 shows a sixth embodiment of the present invention.
  • the feature of this embodiment resides in that the reinforcement is composed only of oblique reinforcements. It should be noted that in this embodiment the same constituent elements as those in the first embodiment are denoted by the same reference numerals as used in the first embodiment, and a description thereof is omitted.
  • Each pad spring 8 has reinforcement 81 provided on the connecting plate 10 thereof.
  • the reinforcement 81 is formed as a recessed projection by a method, for example, embossing, substantially in the same way as in the third embodiment.
  • the reinforcement 81 is, however, composed only of a pair of oblique reinforcements 81 A provided on the inner and outer joint portions 10 B, respectively.
  • the rectilinear reinforcement 15 A in the third embodiment is omitted in this embodiment.
  • the sixth embodiment arranged as stated above can also offer substantially the same advantageous effects as those in the first embodiment.
  • the reinforcements 51 and 71 similar to the reinforcement 15 in the first embodiment are provided on the pad springs 45 and 66 for the disk brakes of the different specifications from those in the first embodiment.
  • the present invention is not necessarily limited to the described arrangement.
  • the reinforcement 21 , 31 or 81 in the second, third or sixth embodiment may be provided on the pad springs 45 and 66 in the fourth and fifth embodiments.
  • two pad springs 8 , 45 or 66 disposed facing each other across the friction pads 7 , 44 or 65 in the rotational direction of the disk D are denoted by the same reference numeral. It should be noted, however, that these two pad springs do not necessarily need to be formed from components of the same configuration but may be formed as components having different configurations from each other.
  • the calipers 3 , 43 and 63 are each slidably supported by the mounting member 1 , 41 or 61 through two sliding pins 5 secured to the caliper.
  • the present invention is not necessarily limited to the described slidably supporting structure.
  • the caliper may be slidably supported by two sliding pins secured to the mounting member, as disclosed in Japanese Patent Application Publication No. Sho 48-41166. It is essential only that the caliper be provided on the mounting member slidably in the axial direction of the disk.
  • reinforcements can be provided on the joint portions (or both the flat plate portion and the joint portions) of the connecting plate of each pad spring.
  • the reinforcements can surely reinforce at least the joint portions and their vicinities.
  • the strength and rigidity of the pad spring between a pair of guide plates can be sufficiently increased without the need to increase the outside dimensions (width and so forth) of the joint portions, for example. Therefore, even if external forces are applied from the caliper or the friction pads to the joint portions of the pad springs in directions in which the joint portions are pulled away from each other during the operation of the disk brake, for example, the joint portions can be prevented from being elastically deformed by the external forces.
  • the pad springs can exhibit their functions stably for an increased period of time, and the durability and reliability thereof can be improved. Further, the increased rigidity of the joint portions can suppress deformation, positional displacement and the like of the guide plates. Consequently, the friction pads can be smoothly displaced along the guide plates, and hence it is possible to minimize the dragging torque and the like of the friction pads and to improve the brake performance. Further, during assembling of the disk brake, the pad springs are unlikely to be deformed even if somewhat strong force is applied thereto to assemble them into the disk brake. Accordingly, the assembling operation can be performed efficiently.
  • the pad springs are stamped from a plate material, for example, it is possible to use a die or the like previously formed with a recessed projection profile for forming reinforcement. With this die, each pad spring is formed, and while doing so, reinforcement having a recessed projection configuration can be formed on the connecting plate by embossing. Thus, the stamping of the pad springs and the formation of the reinforcement can be efficiently performed in the same process.
  • the required strength and rigidity can be readily obtained without the need to complicate the equipment, process, etc. for forming the pad springs, for example.
  • the use of embossing enables a high strength to be obtained without the need to increase the outside dimensions (width and so forth) of the joint portions or to provide bent regions or the like on the joint portions, for example. Accordingly, even when the pad springs are each installed in a narrow gap between the mounting member and the caliper, for example, reinforcement that will not interfere with the surrounding component parts can be formed easily, and the component part shape and the layout components can be designed smoothly.
  • each pad spring can be provided with reinforcement continuously extending over from the flat plate portion to the joint portions, for example.
  • discrete reinforcements can be provided on the flat plate portion and the joint portions, respectively.
  • the connecting plate can be reinforced as a whole by the reinforcement, and the strength and rigidity of the pad spring can be increased even more surely.
  • the rectilinear reinforcement and the oblique reinforcements extend in a substantially U or “]” shape as a whole. Consequently, the connecting plate of the pad spring can be surely reinforced entirely by synergy of the rectilinear reinforcement and the oblique reinforcements, and the strength and rigidity of the pad spring between a pair of guide plates can be further increased.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
US11/790,008 2006-04-28 2007-04-23 Disk brake Active 2028-07-19 US8042656B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2006-126882 2006-04-28
JP126882/2006 2006-04-28
JP2006126882A JP4653010B2 (ja) 2006-04-28 2006-04-28 ディスクブレーキ

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US20070251772A1 US20070251772A1 (en) 2007-11-01
US8042656B2 true US8042656B2 (en) 2011-10-25

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US (1) US8042656B2 (zh)
JP (1) JP4653010B2 (zh)
CN (1) CN101063470B (zh)

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CN101063470B (zh) 2011-04-06
JP4653010B2 (ja) 2011-03-16
US20070251772A1 (en) 2007-11-01
JP2007298119A (ja) 2007-11-15
CN101063470A (zh) 2007-10-31

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